Gyratory crusher



March 25, 1952 H. H. RUMPEL GYRATORY CRUSHER Filed April 7. 1948 INVENTOR.

Patented Mar. 25, 1952 GYRATORY CRUSHER Harvey H. Rumpel, Whitefish Bay, Wis., assignor to Smith Engineering Works, Milwaukee, Wis., a corporation of Wisconsin Application April '7, 1948, Serial No. 19,470

The present invention relates generally to improvements in the crusher art, and relates more specifically to improvements in the construction and operation of gyratory crusher for reducing hard substances such as rock, ore and the like; and this application is a continuation in part of my prior application, Serial No. 729,708, filed February 20, 1947, now abandoned.

The primary object of my invention is to provide an improved gyratory crusher which is simple and durable in structure, and which is also highly eflicient in operation.

Many different types of gyratory crushers for reducing hard substances such as rock and ore, have heretofore been proposed and used extensively, and some of these prior gyratory reduction crushers are operable at high speed and with relatively extensive crushing stroke in order to utilize impact as well as mere pressure in effecting rapid and efficient crushing. These impact gyratory crushers ordinarily employ a relatively long upright eccentric revolvable at high speed within a sturdy frame in order to gyrate a freely rotatable crushing head cooperating with a fixed crushing concave to form an annular outwardly and downwardly flaring crushing zone; and the actuating eccentric of each of these prior machines, is ordinarily mounted upon a stationary thrust bearing coacting with the lower end thereof, while the crushing head coacts with the opposite upper end of the eccentric through a revolving thrust bearing, the intervening portion of the eccentric serving as a guide bearing coacting with the fixed frame and with the head journal shaft. These remotely separated thrust bearings are preferably of the anti-friction type, as shown in my prior Patent No. 1,993,900, granted March 12, 1935, and when the head is gyratable and rotatable about an axis which is inclined relative to the central vertical axis of the eccentric, the stationary thrust bearing is disposed horizontal or perpendicular to this central axis,.while the revolvable thrust bearing is disposed perpendicular to the inclined eccentric axis, that is, at an inclination relative to the horizontal fixed bearing.

It has been discovered, that this widely separated disposition of the thrust bearings associated with the opposite ends of the elongated eccentric, tends to produce uneven loading of the intervening external eccentric guide bearing thus introducing extremely high and excessive local pressures which cause undesirably rapid bearing failures. It has also been found that the wide separation of these thrust bearings and the Canada June 17, 1947 3 Claims. (01. 241216) mounting of the eccentric upon a fixed thrust bearing located remote from the crushing zone,

permits the elongated eccentric to tilt relative to the stationary thrust bearing, thus also causing 5 relatively rapid and non-uniform wear in this thrust bearing and in the outer guide bearing. The location of the other or revolving thrust bearing near the crushing zone and between the head and the eccentric, is however perfectly satisiactory, since the internal eccentric guide bearing cooperates with this movable thrust bearing to positively prevent relative undesirable tilting of these coacting elements.

A proposal has heretofore been made, to eliminate the use of the relatively long internal and external eccentric guide bearings in crushers of this type, by providing ball bearings at the upper and lower ends of the eccentric sleeve separated by a long interveningspace. In this prior pro- 20 posal the eccentric is provided at its upper end with a flange the bottom of which coacts with the frame of the crusher through a ball bearing and the top of which coacts with the head through a similar ball bearing. The lower end of the eccentric also coacts with the crusher frame through an external ball bearing and with the head guiding shaft through an internal ball bearing, and the upper and lower sets of ball bearings are separated by the intervening vertical space which is devoid of contact between the eccentric and the frame and head. The ball bearings alone must therefore resist both the vertical and horizontal components of the enormous crushing pressures, and this is highly impractical because the ball bearings must be made too large and cumbersome to permit installation thereof within the available space. Then too, the ball bearings of this previous proposal were not properly mounted to maintain them accurately centralized relative to their respective axes of rotation, thus introducing further objection to the proposed structure.

It is therefore a more specific object of my present invention to provide an improved bearing assemblage for gyratory crushers, which functions to firmly confine the parts in proper relative position and thus vastly prolongs the life of such machines.

Another specific object of this invention is to provide improved bearings for the head and eccentric of a gyratory impact crusher, which will most effectively resist normal crushing pressures and will also positively eliminate tilting of the eccentric and of the head carried thereby 55 relative to the main frame.

desire or intention to unnecessarily restri scope of utility of the improvement by virtue of v hub 5 and having a renewable liner 5 bore 5; an elongated eccentric it having an outto provide an improved drive for gyrato tion crushers or the like, which is extrei w rable and efiicient in operation, and which may also be quickly and conveniently assemble dismantled.

against rapid wear and other possible damage;

while being susceptible of abundant lubrication, during normal use.

These and other objects and advantages of the invention will be apparent from the following detailed description.

A clear conception of the various features constituting my present improvement, cf the mode of constructing and of operating a typical high speed gyratory reduction crusher, enibedying the invention, may be had by referring to the drawing accompanying and torn a part of this specification, wherein like reference characters designate the saiile or similar par ts.

The Single figure of the drawing is a central vertical section through a typical high speed gyro- .tory crusher embodying my improved head 'porting and gyrating mechanism.

While the invention has been n and described herein as being advantageously applicable to a high speed, long throw gyratory crusher wherein the concave is stationary and the head is supported and gyratable from beneath so as to provide an unobstructed feed inlet, it is not my ct the this limited disclosure.

Referring to the drawing, the high speed gyra- :tory' reduction crusher disclosed therein by way of illustration, comprises in general, a main frame 6 having an integral rigid central hub provided with an upright bore 5 and also having therein an annular crushed material discharge space l; a concave is carried by the frame 1 above the provided ml with a with an annular crushing surface to a central fresh material inlet opening posed coaxial relative to the central axis l2 citli'e' frarce er cylindrical peripheral surface journalled for rotation in the frame bore 6 and also having an internal tapered eccentric bore i5 generated about an axis I5 which is inclined relative to and inter sects the axis 52 near the f ed opening H, the eccentric it being provided with a rigid integral flange ll projecting outwardly from its upper end and over the frame hub 5 and, also having an integral annular extension 29 projecting upwardly beyond the flange 1 l; a lower annular roller-type thrust bearing is interposed between the bottom of the eccentric flange ll and the top of the frame hub 5 and lying in a plane perpendicular to the vertical axis a similar upper annular roller-type thrust bearing disposed directly relative to the axis E a head 25 coacting with the top of t 2 flange ll through the upper thrust bes'ing and having a renewable main mantle co m. provided with an annular crushing surface 23 cooperating with the concave surface it to proe outwardly and downwardly flaring crushzone 2d, the head 2i lso being provided with d central guide shaft 25 iournalled for free rota ..on within tie tapered eccentric bore I5; and. a bevel gear secured to the lower end of e eccentric it and coacting with a driving pinion a: secured to the crusher driving shaft 22.

' :1 frame t should be of sturdy conhuh c has an integral upward s of heavy integral ribs and the upper 1g member or concave 8 is tiltably mountupon a supporting 35 which is vertically ably secured to the outer frame wall by cans of an annular split wedge As shown, the ccrcave liner 9 provided with an approxiustro-conical crushing surface it which on th head mantle to produce the flarannular crushing Zone but these surfaces in to suit different one. The liner 8 is detachably o the concave 5 by bolts 33, and the con- 8 h as an integral peripheral flange 3:? which with and no ally held snugly against formed on the supre ainer 38 which is connectrtin v Si by rods 39, and which er having an outlet alinc l ent with the concave '1 ng abnormal conditions usher, the springs 33 may a permit the concave 8 to My from the 1 ad 2! and to thus prevent age to the unduly tressed crusher parts.

lower portion the concave supporting is int ni y s rew threaded while the ex csi d with an annular es cooperable with the and has an. internal is wedgingly cooperable of lever 5:3 pivotally assoi, operable to revolve about the annular Wedge e or lower the concave't he vertical width of the (50 elements in posil: screws also carried by 1 order to protect the ad i'grit and d1 the con- 5 is also provided with an sealin ly coacts' with uter frame wall around he and wear eccei n wihin th l bore 6 c :ranie hub erably he the flange t" ed integ or rotatio tre I31. u form rel ics with a spherical crushing surface 23.

of this eccentric as well as the major downward pressures exerted thereagainst, are obviously borne by this sturdy flange l1 so that the long frame bore 5 serves primarily only as a guide bearing for preventing lateral displacement of the upright eccentric. The anti-friction thrust bearings i9, 25 between which the flange I1 is interposed, are preferably of the annular roller type, each comprising a series of cylindrical rollers radiating from the bearing axis and having individual axes lying in a common plane; and the plane of the lower roller bearing i9 is disposed perpendicular to the central axis l2 of the eccentric guide bearing bore 6, while the plane of the upper roller bearing 20 is inclined relative to the horizontal and is in fact perpendicular to the central axis Id of the tapered eccentric bore it. The annular roller bearings I9, 26 are accurately positioned and centralized relative to their respective axes by the rigid extensions I8, 29 which also serve to lengthen the guide bearings; and are enclosed by a freely rotatable vertically extending-sealing ring 49 carried by the rigid flange and coacting through labyrinth seals 64, 55

respectively with the bottom of the head 2| and with the top of a wall 50 formed integral with the frame 4 and providing a lubricant chamber 5|. A counterweight 48 which counter-balances the weight of the head 2| relative to the eccentric sleeve I4, is secured to the periphery of the ring 49 between and outwardly beyond the roller thrust bearings l9, 2!} near the upper end of the eccentric. The sealing ring 49 additionally coacts with the interior of the annular stationary frame wall 50 through a snap ring 52, thereby effectively protecting the various thrust and guide bearings against entry of foreign matter and possible escape of lubricant,

While the eccentric i4 is suspended directly from the top of the frame hub 5 by virtue cf the direct coaction of the flange l! with the lower struction of the bevel gear 26 and the attachment thereof to the eccentric M, are somewhat simplified by eliminating all thrust bearings for the eccentric at the bottom thereof, and the bevel pinion 21 which is secured to the inner end of the driving shaft 25 is also housed within the chamber 5|. The horizontal drive shaft 28 is mounted in bearings 60 carried by a tubular bearing box detachably secured to the frame 4, and this shaft 28 may be rotated at any desired speed by means of a pulley or otherwise. In order to insure proper lubrication of all of the bearings. the plate 59, gear 26 and eccentric M are provided with suitable lubricant conducting passages, ports and grooves communicating with the chamber 5|, and through whichlubricant is adapted to be constantly circulated by means of a pump 62 operable by the drive shaft 28 whenever the crusher is operating.

During normal operation of the improved gyratory crusher, when power is applied to the driving pulley 6| and shaft 28, the eccentric M will be rotated through the intermeshing gears 27, 26 to gyrate the head 2|, and the lubricating pump 62 will be simultaneously actuated to circulate abundant lubricant to all of the bearings and motion transmitting gearing. Raw or fresh material delivered to the supply hopper 40 will I gravitate into the crushing zone 24 through the thrust bearing I9, the crushing head 2! is supported directly upon the eccentric M by virtue of similar coaction with the upper thrust bearing 20, thus concentrating the thrust bearings for both the eccentric and the head as near as possible to the crushing zone 24. The head 2| is positively prevented from shifting sidewise relative to the upper thrust bearing 25, by the rigid eccentric extension 29 and by the tapered shaft 25, the latter being rigidly secured to the head and coacting with the guide bearing or eccentric bore |5 but being freely rotatable therein. The main head protecting mantle 22 which has the crushing surface 23 formed thereon and coacting with the frustro-conical crushing surface In of the concave liner 9 to produce the crushing zone 24, is adapted to be firmly secured to the head 2| by means of a mantle attaching stud 53 and nut 54 coacting with an auxiliary upper mantle section 55, and these fastening elements may be protected by means of a cap 56, as shown.

Although the crushing head 2| is freely rotatable relative to the crushing concave'il and to the eccentric hi, the latter is positively rotatable at any desired speed, by means of the gearing coactingwith the lower extremity of the eccentric. The bevel gear 26 is firmly but detachably secured to the bottom of the eccentric l4 by one or more cap screws 58 and a radial key 5? shown in crosssection near the axis l2 relieves these cap screws of shear, and the gear 26 is enclosed within the lubricant confining chamber 5| by a bottom closure plate 59 removal of which gives free access to the gear 26 and pinion 21. The contil central inlet opening I l of the concave liner 8, and will gradually advance downwardly and outwardly through this zone 24, being reduced or I crushed as it proceeds, by the gyrating head 2| cooperating with the normally fixed concave 8. The finally reduced material is eventually delivered from the annular outlet opening at the discharge end of the zone 24, and drops by gravity through the annular space and slides down the inclined surfaces of the shields 41 to suitabl receptacles.

During this reduction of the material, the head 2| and its retaining shaft 25 are free to either revolve with the constantly rotating eccentric l4 and extension 29, or to revolve reversely of the direction or rotation of the eccentric, or to remain fixed with respect to the head axis IE, but the head 2| will be constantly'gyrated about the central crusher axis |2 whenever the eccentric is rotating. The major downward pressures exerted upon the head 2| as well as the weight of the eccentric l4 and gear 26, will obviously be borne by the roller thrust bearings I9, 28, and the long guide bearings for the eccentric l4 and shaft 25 afforded by the frame and eccentric bores 5, l5 and by the extensions I8, 25, will be subjected to very slight components of downward pressure and to other components of horizontal or lateral pressure distributed uniformly throughout the extensive areas of these guide bearings. While the roller thrust bearings 20,

'l9 will obviously permit radial displacement of the head 2| and eccentric sleeve M in order to compensate for looseness or wear in the guide bearings I5, 6, the eccentric and hub extensions 29, I8 will also resist any tendency of the thrust bearings i9, 20 to shift laterally to any undesirable extent and will thus maintain these annular bearings generally centralized relative to their respective axes l2, It. If abnormal pressure develops Within the crushing zone 24, the springs 35 will promptly function to relieve such pressures by permitting the concave 8 to rise or tilt with respect to the supporting ring 3|, and the degree of reduction of the material may be readily varied by raising or lowering the concave 8 may occur to persons sir also intended that specific --e increasing or diminishing the the crushing zone 2%.

From the fore' oiing detailed be apparent that in r sent provides a new ion and disposition of th and their coaction with the trio and frame extensio and minimum power consd' u distributing the vet seal and h nents of the crush ur t lubrication o prori i a suppo t 2i manufact cinissi I ,r all of eccentric tensic lower removal of the above, t ad bill structed, has enormous capac iii-sited occupied, is c to produce c1 and con -.ining minimum iiy manufactured to inoperation.

appended .own and decor hin the soap I claim:

1. In a gyratory crusher, a frame having an upright central bore, a normally radialiy loaded bearing extending substantially throughout the length of said frame bore, normally stationary crushing concave carried by said frame coaxially 3 rollers interposed directly between the bottom or" said flange and an upper surface of said frame outwardly beyond said frame bearing and constituting the sole means for supporting the 5 weight or said sieeve and of the elements resting thereon, a or sleeve and having a rigidly attached depending shaft jcurne d for free rotation within said '0 bee 1g and also having an upper surlO face cooperating with concave to provide an annular dew; wardly and outwardly flaring crushing ch pper, an upper thrust bearing coma annular series of radial rollers interen said head and an upper bet-we 15 surface flange outwardly beyond said eccentric a vertically extending ring surge and having a sealingmeans e the ring and also having sealin means between said head and and a co rterweight for said head asso- 1e p riphery of said ring between s. v are y crusher, a frame having an core, a normally radially loaded ca 1g substantially throughout the rarce bore, a normally stationary ve carried said frame coaxially core, a sleeve journalled for rotaframe bearing and having an eccenar irs of which intersects the axis ing above said sleeve, a norbearing extending substanlength of said eccentric bore, .g a single rigid upper flange pro- 'eriiiy over the upper end of said a lower thrust searing interposed between the bot-torn of said flange and an said frame outwardly beyond and constituting the sole the weight or said sleeve thereon, said lower annular series of radial perpendicular to said reed above said sice". e

ee-ting obare,

l. dly beyond said eccentric t'rr' bearing having an roll rs lying in a plane sic on e, a vertically flange and having searing hi ring and also having additional sealing means between said head and est bearings.

e having a rigid an upright bore, a

g extending sub- .l of-said frame bore, a normally st I shin concave carried by s is l frame bore, a sleeve journalled f on in frame auier u per extenl1}; radially a nular loaded e,

out the length said e having a sir de rigid u g projecting outom beneath the top of its said extension bore, a lower thrust bearing comprising an annular series of radial cylindrical rollers surrounding said frame extension and being interposed directly between the bottom of said flange and an upper surface of said frame outwardly beyond said frame bearing and constituting the sole means for supporting the weight of said sleeve and of the elements resting thereon, a crushing head disposed above said sleeve and having a rigidly attached depending shaft journalled for free rotation within said eccentric bearing and also having an upper surface cooperating with said concave to provide an annular downwardly and outwardly flaring crushing chamber, an upper thrust bearing comprising an annular series of radial cylindrical rollers surrounding said sleeve extension and being interposed directly between said head and an upper surface of said flange outwardly beyond said eccentric bearing, a vertically extending ring surrounding said flange and having sealing means between saidframe and the ring and also having additional sealing means between said head and the ring, and a counterweight for said head suspended from the periphery of said ring between said thrust bearings.

HARVEY H. RUMPEL.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,000,049 Symons Aug. 8, 1911 1,031,083 Newhouse July 2, 1912 1,083,283 Kelly Jan. 6, 1914 1,537,564 Symons May 12, 1925 1,575,874 Symons Mar. 9, 1926 1,609,594 Anderson Dec. '7, 1926 1,993,900 Rumpel Mar. 12, 1935 2,110,276 Rumpel Mar. 8, 1938 2,185,528 Stevens Jan. 2, 1940 2,231,491 Bousman Feb. 11, 1941 FOREIGN PATENTS Number Country Date 673,351 Germany Mar. 20, 1939 66,645 Norway Aug. 16, 1943 

